CN113176721A

CN113176721A - Clock and watch

Info

Publication number: CN113176721A
Application number: CN202110096089.6A
Authority: CN
Inventors: 林茂之
Original assignee: Seiko Epson Corp
Current assignee: Seiko Epson Corp
Priority date: 2020-01-27
Filing date: 2021-01-25
Publication date: 2021-07-27
Anticipated expiration: 2041-01-25
Also published as: US11835924B2; EP3855253A1; CN118778404A; EP3855253B1; JP2021117111A; CN113176721B; JP7327181B2; US20210232094A1

Abstract

Provided is a timepiece which suppresses increase in the size and thickness of a flat surface and has a long duration. The timepiece is characterized by comprising: a1 st drum having a1 st shaft, a1 st spring, and a1 st barrel; and a2 nd barrel wheel having a2 nd shaft, a2 nd spring, and a2 nd barrel, arranged in a plane direction perpendicular to the axial direction of the 1 st shaft, and transmitting the rotation of the 1 st barrel wheel to the 2 nd barrel wheel. The diameter of the addendum circle of the 1 st drum is smaller than that of the 2 nd drum, and the thickness of the 1 st drum is thicker than that of the 2 nd drum.

Description

Clock and watch

Technical Field

The present invention relates to timepieces.

Background

Patent document 1 discloses a timepiece having two barrels. In this timepiece, two barrels are coaxially stacked or arranged in the same plane.

Patent document 1: japanese laid-open patent publication No. 51-46161

A timepiece having a structure in which two barrels are stacked becomes thick. In the structure in which the two barrels are arranged in the same plane, since the plane sizes of the two barrels are substantially the same, the ratio of the barrels to the movement becomes large, and a useless empty space is generated around the barrels.

Disclosure of Invention

The timepiece of the present disclosure is characterized by having: a1 st drum having a1 st shaft, a1 st spring, and a1 st barrel; and a2 nd barrel including a2 nd shaft, a2 nd spring, and a2 nd barrel, arranged in a plane direction perpendicular to an axial direction of the 1 st shaft, wherein rotation of the 1 st barrel is transmitted to the 2 nd barrel, a tip diameter of the 1 st barrel is smaller than a tip diameter of the 2 nd barrel, and a thickness of the 1 st barrel is thicker than a thickness of the 2 nd barrel.

Drawings

Fig. 1 is a front view of a timepiece showing an embodiment.

Fig. 2 is a rear view showing the timepiece.

Fig. 3 is a plan view showing a main part of the timepiece movement.

Fig. 4 is a plan view showing a main part of the timepiece movement.

Fig. 5 is a sectional view showing a main part of the timepiece movement.

Fig. 6 is a cross-sectional view showing a main part of the timepiece movement.

Fig. 7 is a cross-sectional view showing a main part of the timepiece movement.

Fig. 8 is a perspective view showing a main part of the timepiece movement.

Fig. 9 is a perspective view showing a main part of the timepiece movement.

Fig. 10 is a cross-sectional view showing the 1 st and 2 nd reels of the timepiece.

Description of the reference symbols

1: a timepiece; 2: an outer case; 3: a dial plate; 3A: a calendar small window; 3B: time marking; 4A: a hour hand; 4B: needle separation; 4C: a second hand; 5: an energy storage needle; 6: a date wheel; 7: a crown; 10: a movement; 11: a base plate; 13: a second splint; 14: a gear train splint; 20: the 1 st spring; 21: the 1 st box roller; 22: the 1 st box; 23: the 1 st shaft; 24: 1 st large steel wheel; 27: a middle wheel of the strip box; 30: the 2 nd spring; 31: the 2 nd reel; 32: the 2 nd cartridge; 33: a2 nd shaft; 34: the 2 nd large steel wheel; 35: a sliding attachment; 40: a manual winding mechanism; 41: a stem; 42: a clutch wheel; 43: vertical wheels; 44: a small steel wheel; 45: a square hole 1 st driving wheel; 46: a square hole 2 nd transmission wheel; 47: a square hole 3 rd transmission wheel; 50: an automatic winding mechanism; 51: a rotary hammer; 52: a bearing; 53: an eccentric wheel; 54: a claw rod; 55: a driving wheel; 60: a planetary gear mechanism; 61: 1 st sun gear; 62: a2 nd sun gear; 63: a planet intermediate wheel; 64: a planet wheel; 66: winding mark wheels; 70: an energy storage wheel train; 71: a winding display wheel train; 711: the 1 st planetary transmission wheel; 712: 2 nd planetary transmission wheel; 713: a3 rd planetary transmission wheel; 714: a 4 th planetary transmission wheel; 715: a 5 th planetary transmission wheel; 716: the 6 th planetary transmission wheel; 716A: a pinion gear; 76: loosening the display wheel train; 77: a 7 th planetary transmission wheel; 77A: a pinion gear; 78: the 8 th planetary transmission wheel; 78A: a pinion gear; 80: a generator; 81: a rotor; 81A: a rotor magnet; 81B: a rotor pinion gear; 81C: a rotor inertia circular plate; 82. 83: a coil block; 90: a display wheel train; 92: a second wheel; 93: a third wheel; 94: a fourth wheel; 95: a fifth wheel; 96: a sixth wheel; 97: a time wheel; 97A: an intermediate wheel; 98: a day changing wheel; 99: a date positioning rod; 100: a shaft member; 511: a weight; 512: a hammer body; 512A: an opening; 521: a rotary hammer gear; 531: an eccentric gear; 532: an eccentric shaft member; 551: a drive axle; 552: 1 st driving gear; 553: a2 nd transmission gear; 611: a display shaft; 612: 1 st sun gear; 613: 1 st pinion gear; 621: a2 nd sun gear; 622: a2 nd sun pinion; 632: a rotating shaft; 641: a planetary gear; 642: a planet pinion gear; 661: a1 st gear; 662: a2 nd gear; 663: a shaft; 665: a gear; 941: a second hand shaft; 942: a fourth gear; 943: pinion four.

Detailed Description

[ embodiment ]

Hereinafter, a timepiece 1 according to an embodiment of the present disclosure will be described with reference to the drawings. In the description of the present embodiment, the plan view refers to a state viewed from a direction along the 1 st axis 23 and the 2 nd axis 33 (i.e., a direction perpendicular to the dial 3) described later, and the side view refers to a state viewed from a direction perpendicular to the 1 st axis 23 and the 2 nd axis 33.

Fig. 1 is a front view showing the timepiece 1, and fig. 2 is a rear view showing the timepiece 1. The timepiece 1 of the present embodiment is a hollow-out timepiece in which the power storing hand 5 can be seen from the back surface side of the timepiece 1.

The timepiece 1 is a wristwatch to be worn on a user's wrist, and includes a cylindrical outer case 2, and a dial 3 is disposed on an inner peripheral side of the outer case 2. Of the two openings of the outer case 2, the opening on the front side is covered with a glass cover, and the opening on the rear side is covered with a rear cover 8. The rear cover 8 is composed of an annular frame 8A and a rear cover glass 8B attached to the frame 8A.

The timepiece 1 includes: a movement 10 shown in fig. 3 to 9 housed in the outer case 2; an hour hand 4A, a minute hand 4B, and a second hand 4C indicating time information shown in fig. 1; and a power accumulating needle 5 shown in fig. 2 for indicating the winding margin of the power spring. A calendar window 3A is provided in the dial 3, and the date wheel 6 can be seen through the calendar window 3A. The dial 3 is provided with a time scale 3B for indicating time. Note that the scale 3B is an example of the scale of the present disclosure.

An opening 512A is formed in the hammer body 512 of the rotary hammer 51 shown in fig. 2, and is configured to reduce the number of cases in which the charging needle 5 cannot be seen due to the position of the rotary hammer 51.

A fan-shaped graduation portion 14A is provided on the rear surface of a gear train bridge 14 described later. The power storing needle 5 indicates the scale portion 14A, and thereby the winding amount of the power spring can be displayed.

A crown 7 is provided on a side surface of the outer case 2. Crown 7 can be pulled out from the level 0 position pressed in toward the center of timepiece 1 to the level 1 position and the level 2 position.

When crown 7 is rotated at the 0-stage position, as described later, winding 1 st spring 20 and winding 2 nd spring 30 provided in movement 10 can be wound up. Power accumulating needle 5 moves in conjunction with the winding of winding spring 1 and winding

spring

2, 20. Timepiece 1 of the present embodiment can secure a duration of about 120 hours when winding 1 st spring 20 and winding 2 nd spring 30 are completely wound.

When the crown 7 is pulled to the 1-stage position and rotated, the date wheel 6 can be moved to align the date. When the crown 7 is pulled to the 2-step position, the second hand 4C stops, and when the crown 7 is rotated at the 2-step position, the hour hand 4A and the minute hand 4B move to align the time. The method of correcting the date indicator 6, the hour indicator 4A, and the minute indicator 4B by the crown 7 is the same as that of the conventional mechanical timepiece, and therefore, the description thereof is omitted.

[ movement ]

Next, the movement 10 will be described with reference to fig. 3 to 10. Fig. 3 is a plan view of a main part of movement 10 as viewed from dial 3 side, and fig. 4 is a plan view of a main part of movement 10 as viewed from back cover 8 side. Fig. 5 to 7 are sectional views of main parts of the movement 10, and fig. 8 and 9 are perspective views showing the main parts of the movement 10. Fig. 10 is a cross-sectional view showing the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 as the drive source of the movement 10.

Movement 10 has a1 st barrel 21 housing a1 st clockwork spring 20 and a2 nd barrel 31 housing a2 nd clockwork spring 30. As described later, the hour hand 4A, minute hand 4B, and second hand 4C are attached to the hour wheel 97, minute wheel 921, and second hand shaft 941 of the movement 10, respectively, and are driven by the 1 st spring 20 and the 2 nd spring 30 of the movement 10.

As shown in fig. 5 to 7, the movement 10 has a base plate 11, a second bridge 13, and a train wheel bridge 14. As shown in fig. 4, disposed between the base plate 11 and the train wheel bridge 14 are: a1 st barrel 21 for storing the 1 st power spring 20; a2 nd barrel 31 for storing the 2 nd spring 30; and a manual winding mechanism 40 and an automatic winding mechanism 50 that wind up winding 1 st spring 20 and winding 2 nd spring 30. Further, between the bottom plate 11, the second bridge 13, and the train wheel bridge 14, there are disposed: an energy storage display mechanism for displaying the winding allowance of the 1 st power spring 20 and the 2 nd power spring 30; display train 90 for transmitting torque of the 1 st spring 20 and the 2 nd spring 30; and a generator 80 driven by torque transmitted through the display train 90.

Here, in the present embodiment, as shown in fig. 2 and 5, the weight 511 and the train wheel bridge 14 are disposed at positions that do not overlap when viewed in a plan view, and are disposed so as to partially overlap when viewed in a side view. Therefore, the thickness of timepiece 1 can be made thinner than the case where weight 511 and train wheel bridge 14 are arranged in the thickness direction of timepiece 1.

[ 1 st spring and 1 st barrel wheel ]

Winding 1 st spring 20 is housed in winding 1 st drum 21. Thus, barrel 1, drum 21 has barrel 1, drum 22 and shaft 1, 23. As shown in fig. 8, a1 st large sheave 24 that rotates integrally with the 1 st shaft 23 is attached to the 1 st shaft 23.

[ Manual winding mechanism ]

As shown in fig. 4 and 8, the manual winding mechanism 40 includes a stem 41 to which the crown 7 is attached, a clutch wheel 42, a vertical wheel 43, a small steel wheel 44, a square-hole 1 st transmission wheel 45, a square-hole 2 nd transmission wheel 46, and a square-hole 3 rd transmission wheel 47. The square hole 3 rd transmission wheel 47 is meshed with the 1 st big steel wheel 24.

Therefore, when the crown 7 is rotationally operated by the user at the 0-stage position, the stem 41 and the clutch wheel 42 are rotated. When the crown 7 is at the 0-stage position, the clutch pulley 42 engages with the vertical pulley 43, and the rotation of the clutch pulley 42 is transmitted from the vertical pulley 43 to the small steel pulley 44, the square-hole 1 st transmission wheel 45, the square-hole 2 nd transmission wheel 46, and the square-hole 3 rd transmission wheel 47 in this order. Consequently, 1 st sheave 24 and 1 st shaft 23 rotate, and 1 st spring 20 is wound up.

The square hole 2 nd transmission wheel 46 is a wheel with an internal thread, and by inserting a driver or the like into the internal thread and rotating, the 1 st spring 20 can be tightened. Therefore, winding of 1 st spring 20 can be performed at the time of assembling movement 10, and convenience is not impaired even if the square-hole thread is not disposed.

[ automatic winding mechanism ]

The automatic winding mechanism 50 includes: a rotary hammer 51 shown in fig. 2 and 5; the bearing 52 shown in fig. 2 and 6; an eccentric wheel 53 shown in fig. 4 and 6 engaged with a rotary hammer gear 521 on the outer ring of the bearing 52; a claw lever 54; and a transmission wheel 55.

The rotary hammer 51 has a weight 511 and a hammer body 512.

The bearing 52 rotatably supports the rotary hammer 51, and has a rotary hammer gear 521 on an outer periphery thereof to rotate integrally with the rotary hammer 51.

As shown in fig. 6, the eccentric wheel 53 has an eccentric shaft member 532 and an eccentric gear 531. The eccentric shaft member 532 is pivotally supported by the base plate 11 and the train wheel bridge 14. The eccentric shaft member 532 has an eccentric shaft portion provided eccentrically from the rotation shaft.

The eccentric gear 531 is engaged with the rotary hammer gear 521 of the bearing 52. Thereby, the eccentric 53 rotates in both forward and reverse directions in conjunction with the rotary hammer 51.

The pawl lever 54 is rotatably attached to the eccentric shaft portion of the eccentric shaft member 532 of the eccentric wheel 53.

When the eccentric wheel 53 is rotated in conjunction with the rotary hammer 51, the claw lever 54 attached to the eccentric wheel 53 is advanced and retreated in a direction approaching and separating from the transmission wheel 55, and the transmission wheel 55 is rotated in one direction.

As shown in FIG. 6, the drive wheel 55 has a drive wheel shaft 551, a1 st drive gear 552 and a2 nd drive gear 553.

The transfer wheel shaft 551 is supported by the base plate 11 and the train wheel bridge 14. The 1 st transmission gear 552 is engaged with the pawl lever 54, and the transmission gear 55 rotates in one direction in conjunction with the forward and backward movement of the pawl lever 54. And, the 2 nd transmission gear 553 is engaged with the 1 st large steel wheel 24. Thereby, the 1 st large steel wheel 24 rotates in conjunction with the rotation of the transmission wheel 55. When the 1 st large steel wheel 24 rotates, the 1 st shaft 23 rotates integrally with the 1 st large steel wheel 24, and the 1 st spring 20 is wound up.

Therefore, timepiece 1 of the present embodiment can wind up 1 st spring 20 by both manual winding by operating crown 7 and automatic winding by rotating rotary hammer 51. The transmission wheel 55 is a winding wheel engaged with the 1 st large steel wheel 24 in the automatic winding mechanism 50.

[ 2 nd spring and 2 nd barrel ]

As shown in fig. 4 and 5, the 2 nd spring 30 is housed in the 2 nd drum 31. The 2 nd barrel 31 has a2 nd barrel 32 and a2 nd shaft 33. The 2 nd shaft 33 is rotatable integrally with the 2 nd large steel wheel 34.

Winding 2 spring 30 is wound up by winding 1 spring 20. That is, when the 1 st barrel 20 is wound up and torque capable of winding up the 2 nd barrel 30 is accumulated, the 1 st barrel 22 of the 1 st barrel 21 rotates. Barrel 1, through barrel intermediate wheel 27, engages with large 2 steel wheel 34 of

barrel

2, 31, and when barrel 1 rotates, large 2 steel wheel 34 and shaft 2 33 rotate, thereby winding up spring 2 30.

Therefore, in timepiece 1 of the present embodiment, both winding 1 st spring 20 and winding 2 nd spring 30 can be wound by either of manual winding mechanism 40 and automatic winding mechanism 50. In addition, as timepiece 1, only one of manual winding mechanism 40 and automatic winding mechanism 50 may be provided.

Further, the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 are disposed in one of two regions virtually dividing the bottom plate 11 into two in the axial direction of the stem 41. The axial direction of the stem 41 is the direction of the timing mark 3B connecting the 3 nd and 9 th time of the dial 3, and the bottom plate 11 is virtually divided into two areas, the 12 th time side and the 6 th time side. In the present embodiment, a region on the 6 th time side of the two regions will be described as a1 st region, and a region on the 12 th time side will be described as a2 nd region.

Here, in the timepiece 1 of the present embodiment, as shown in fig. 4, the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 are arranged at positions where they do not overlap each other in a plan view in the 2 nd region, which is the region on the 12 th hour side. Further, the present invention is not limited to the above configuration, and for example, the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 may be disposed in the 1 st region.

[ energy storage display mechanism ]

Timepiece 1 has an energy storage display mechanism that displays the winding allowance of 1

st power spring

20 and 2 nd power spring 30 as a driving source. The energy accumulation display mechanism has a planetary gear mechanism 60, an energy accumulation train 70, a sector graduation portion 14A arranged on a train wheel bridge 14 shown in fig. 2, and an energy accumulation hand 5. The scale portion 14A is marked with a substantially band-shaped scale indicated by the power storing needle 5. Further, since the duration of timepiece 1 can be estimated from the winding remaining amounts of 1

st power spring

20 and 2 nd power spring 30 as the drive sources, the duration can be indicated by power storing hand 5 by printing a number indicating the duration on scale portion 14A.

As shown in fig. 8, the power train 70 has a winding display train 71 and a release display train 76.

The winding display gear train 71 has a1 st planetary drive wheel 711, a2 nd planetary drive wheel 712, a3 rd planetary drive wheel 713, a 4 th planetary drive wheel 714, a 5 th planetary drive wheel 715 and a 6 th planetary drive wheel 716. The 1 st planetary driving wheel 711 is engaged with the 2 nd transmission gear 553, and when the 1 st large steel wheel 24 is rotated by the manual winding mechanism 40 or the automatic winding mechanism 50, the 1 st large steel wheel 24, the 2 nd transmission gear 553, the 1 st planetary driving wheel 711, the 2 nd planetary driving wheel 712, the 3 rd planetary driving wheel 713, the 4 th planetary driving wheel 714, the 5 th planetary driving wheel 715 and the 6 th planetary driving wheel 716 are rotated in linkage. As shown in fig. 4, a pinion gear 716A that meshes with the planetary gear mechanism 60 is provided on the rotation shaft of the 6 th planetary drive wheel 716.

The 1 st planetary transmission wheel 711, the 2 nd planetary transmission wheel 712, the 3 rd planetary transmission wheel 713, the 4 th planetary transmission wheel 714 and the 5 th planetary transmission wheel 715 are arranged at positions overlapping with the 2 nd barrel wheel 31 in a plan view. The 1 st planetary transmission wheel 711 to the 5 th planetary transmission wheel 715 are arranged along the periphery of the 2 nd shaft 33 of the 2 nd drum 31 and at positions not overlapping the 2 nd shaft 33 in plan view.

As shown in fig. 4 and 8, the release display train 76 has a 7 th planetary drive wheel 77 and an 8 th planetary drive wheel 78. The 7 th planetary transmission wheel 77 has a pinion 77A meshing with the 8 th planetary transmission wheel 78, and the 8 th planetary transmission wheel 78 has a pinion 78A meshing with the planetary gear mechanism 60. The 7 th planetary transmission wheel 77 is engaged with the 2 nd can 32, and when the 2 nd can 32 rotates, the 7 th planetary transmission wheel 77 and the 8 th planetary transmission wheel 78 rotate in a linkage manner.

The 7 th planetary transmission wheel 77 and the 8 th planetary transmission wheel 78 are rotatably supported by the base plate 11 and the second bridge 13.

As shown in fig. 4, 5, and 8, the planetary gear mechanism 60 includes a1 st sun gear 61, a2 nd sun gear 62, a planetary intermediate gear 63, and a planetary gear 64 rotatably supported by the planetary intermediate gear 63.

As shown in fig. 5, the 1 st sun gear 61 includes a display shaft 611 rotatably supported by the base plate 11 or the like, and a1 st sun gear 612 fixed to the display shaft 611. A1 st pinion gear 613 is integrally formed at a1 st end portion of the display shaft 611 on the dial 3 side. A2 nd pinion 614 is attached to the 2 nd end of the display shaft 611 on the rear cover side. These 1

st pinion gear

613 and 2 nd pinion gear 614 rotate integrally with the display shaft 611 and the 1 st sun gear 612.

As shown in fig. 5, the winding index wheel 66 has a1 st gear 661, a2 nd gear 662, and a shaft 663. The 1 st gear 661 is formed in a substantially semicircular shape in plan and is a gear that meshes with the 2 nd pinion gear 614. The 2 nd gear 662 is a gear that meshes with a gear 665 that is pivotally supported by the second bridge 13. The gear 665 is provided to eliminate gear backlash between the winding flag wheel 66 and the 2 nd pinion 614. The side surface of the gear 665 is urged by a spring, not shown, which applies a force in the unwinding direction of the 2 nd spring 30, and the winding indicator 66 is returned in the unwinding direction of the 2 nd spring 30 via the gear 665. With this structure, the indication deviation of the energy storage needle 5 can be suppressed to be small. Further, the spring for eliminating the backlash may not be provided. In fig. 4, the gear 665 is not shown.

Here, in the present embodiment, as shown in fig. 5, a part of the second bridge 13 that pivotally supports the winding indicator wheel 66 is disposed between the weight 511 and the bottom plate 11. That is, the second plate 13 is disposed so that a part thereof overlaps the weight 511 when viewed in plan. Thus, the 7 th planetary gear wheel 77 and the 8 th planetary gear wheel 78 of the loosening indication gear train 76 are disposed in the space on the bottom plate 11 side of the weight 511, and they can be supported by the bottom plate 11 and the second bridge 13. Therefore, in the present embodiment, as compared with the case where weight 511 and second bridge 13 are arranged so as not to overlap in plan view, the internal space of case 2 can be effectively utilized, and timepiece 1 can be made compact.

The power accumulating needle 5 is mounted on the shaft 663 of the winding index wheel 66. Therefore, the winding indicator wheel 66 is driven by the 2 nd pinion 614, and the power storage needle 5 is configured to rotate in conjunction with the rotation of the 1 st sun gear 61.

Here, in the present embodiment, as shown in fig. 2 and 5, the energy accumulating needle 5 is disposed in the concave portion 14B formed in the train wheel bridge 14, the energy accumulating needle 5 is disposed at a position not overlapping with the weight 511 in a plan view, and the energy accumulating needle 5 is disposed at a position overlapping with the train wheel bridge 14 in a side view. Thus, even if the weight 511 and the power pin 5 are not arranged in the thickness direction of the timepiece 1, interference between the weight 511 and the power pin 5 can be prevented.

The 2 nd sun gear 62 has a2 nd sun gear 621 and a2 nd sun pinion 622 fixed to the 2 nd sun gear 621. The 2 nd sun pinion 622 is rotatably supported by the display shaft 611, and thereby the 2 nd sun gear 62 is disposed coaxially with and rotatably supported by the 1 st sun gear 61.

The planetary intermediate gear 63 is rotatably supported by the display shaft 611 and is coaxial with the 1 st sun gear 61 and the 2 nd sun gear 62. Teeth that mesh with the pinion 78A of the 8 th planetary transmission wheel 78 are formed on the outer periphery of the planetary intermediate wheel 63. A pin-shaped rotation shaft 632 is fixed at a position eccentric to the rotation shaft of the planet intermediate wheel 63.

The planetary gear 64 has a planetary gear 641 and a planetary pinion 642 integrally fixed to the planetary gear 641, and the planetary gear 64 is rotatably supported by the rotary shaft 632 of the planetary intermediate gear 63.

The planet gears 641 are meshed with the 2 nd sun pinion 622, and the planet pinions 642 are meshed with the 1 st sun gear 612.

[ operation of energy storage display mechanism ]

In such a stored energy display mechanism, the operation at the time of winding and unwinding of 1

st spring

20 and 2 nd spring 30 will be described.

When 1 st large drum 24 is rotated by manual winding mechanism 40 and automatic winding mechanism 50, 1 st shaft 23 is rotated to wind 1 st spring 20. Further, as the 1 st shaft 23 rotates, the 1 st planetary gear 711, the 2 nd planetary gear 712, the 3 rd planetary gear 713, the 4 th planetary gear 714, the 5 th planetary gear 715, and the 6 th planetary gear 716 of the winding display gear train 71 rotate, and the torque thereof is transmitted to the 2 nd sun gear 62, the planetary gears 64, and the 1 st sun gear 61. Here, at the time of winding up spring 1 and before winding up spring 2 completely by spring 120, drum 2 32 of drum 2 31 rotates slowly and is in a substantially stopped state, and therefore,

planetary transmission wheels

7 and 8 of unwinding display train 76 and planetary intermediate wheel 63 meshing with pinion 78A of planetary transmission wheel 8 are in a stopped state. Therefore, the planetary gear 64 that is pivotally supported by the rotation shaft 632 of the planetary intermediate gear 63 rotates (i.e., rotates) on its own, and the 1 st sun gear 61 and the display shaft 611 rotate in the 1 st direction. When the 1 st sun gear 61 and the display shaft 611 rotate in the 1 st direction, the winding indicator 66 rotates via the 2 nd pinion 614, and the power storing needle 5 rotates counterclockwise, that is, in a direction in which the winding remaining amount of the power spring displayed by indicating the scale of the scale section 14A increases.

When winding 1 st spring 20 and winding 2 nd spring 30 are unwound, 1 st large wheel 24 and winding display train 71 are stopped, and therefore 2 nd sun gear 62 is also stopped. Also, when barrel 2 32 is rotated by unwinding of spring 2, its torque is transmitted to planetary intermediate gear 63 via planetary transmission wheel 7 and planetary transmission wheel 8 78 of unwinding display train 76. When the planet intermediate wheel 63 rotates, the 2 nd sun pinion 622 that meshes with the planet gear 641 of the planet wheel 64 stops, and therefore the planet wheel 64 rotates and revolves around the 2 nd sun pinion 622. Thereby, the 1 st sun gear 612 meshing with the planetary gear 64 rotates in the 2 nd direction, which is the opposite direction to the winding operation of the 1 st and 2 nd balance springs 20 and 30. When the 1 st sun gear 612 rotates in the 2 nd direction, the display shaft 611 also rotates in the 2 nd direction and is transmitted to the winding indicator wheel 66 via the 2 nd pinion 614, and the power storing needle 5 rotates in the clockwise direction, which is the opposite direction to that in the winding operation.

[ Generator ]

As shown in fig. 4, the generator 80 is configured to have a rotor 81 and coil blocks 82 and 83. The rotor 81 includes a rotor magnet 81A, a rotor pinion gear 81B, and a rotor inertia disk 81C. The rotor inertia disk 81C reduces the variation in the rotational speed of the rotor 81 due to the variation in the driving torque from the 2 nd barrel 32. The coil blocks 82 and 83 are each configured by winding a coil around each core.

Therefore, when the rotor 81 is rotated by the torque from the outside, the generator 80 can generate the induced power by the coil blocks 82 and 83, output the electric energy, and supply the electric energy to the IC or the like. Further, the braking can be applied to the rotor 81 by short-circuiting the coils, and the rotational cycle of the rotor 81 can be adjusted to be constant by controlling the braking force.

In this way, the timepiece 1 of the present embodiment is configured as an electronically controlled mechanical timepiece including the generator 80, and the generator 80 generates induced electric power and outputs electric energy and is also used as a speed adjusting mechanism.

In the present embodiment, when the bottom plate 11 is divided into the 12 th and 6 th stages, the generator 80 is disposed in the 6 th stage region (i.e., the 1 st region different from the 2 nd region on the 12 th stage side where the 1 st and 2 nd barrels 21 and 31 are disposed).

[ display wheel train ]

Next, the display train 90 for driving the hour hand 4A, minute hand 4B, and second hand 4C by the mechanical energy from the 1 st spring 20 and the 2 nd spring 30 will be described.

As shown in fig. 4, 7, and 8, the display train 90 includes a second wheel 92, a third wheel 93, a fourth wheel 94, a fifth wheel 95, and a sixth wheel 96. The rotation of the 2 nd barrel 32 is transmitted to the second pulley 92, and then sequentially increased in speed by the third pulley 93, the fourth pulley 94, the fifth pulley 95, and the sixth pulley 96, and then transmitted to the rotor 81.

As shown in fig. 7, the minute hand 4B is fixed to the second wheel 92 via a minute wheel 921.

The fourth wheel 94 has a second hand shaft 941 for fixing the second hand 4C, a fourth gear 942 meshing with the fifth wheel 95, and a fourth pinion 943 meshing with the third wheel 93. In the present embodiment, the second shaft 941 of the fourth wheel 94 is pivotally supported by the train wheel bridge 14 and is pivotally supported by the base plate 11 via the minute wheel 921. The fourth wheel 94 is an example of the seconds wheel of the present disclosure.

An hour wheel 97 is connected to the minute wheel 921 via a jumper wheel not shown, and an hour hand 4A is fixed to the hour wheel 97.

A day change intermediate wheel 97A is attached to the hour wheel 97, and a day change claw for rotating the date wheel 6 is attached to the day change wheel 98 rotated by the day change intermediate wheel 97A.

Date indicator lever 99 for suppressing the play of date wheel 6 is engaged with the internal teeth of date wheel 6. In the present embodiment, date jumper 99 is swingably attached via a shaft member 100 attached to base plate 11.

In the timepiece 1 described above, the ac output from the generator 80 is boosted and rectified by the rectifier circuit including boost rectification, full-wave rectification, half-wave rectification, transistor rectification, and the like, and charged in the smoothing capacitor, and the rotation control device, not shown, that controls the rotation period of the generator 80 is operated by the electric power from the capacitor. The rotation control device is constituted by an integrated circuit including an oscillation circuit, a frequency dividing circuit, a rotation detection circuit, a rotation speed comparison circuit, an electromagnetic brake control unit, and the like, and the oscillation circuit uses a quartz resonator.

[ configuration of the fourth wheel and the eccentric wheel ]

As shown in fig. 4, in the present embodiment, the seconds shaft 941 of the fourth wheel 94 and the eccentric shaft 532 of the eccentric wheel 53 are disposed at positions not overlapping each other in plan view. As described above, as shown in fig. 6, the eccentric shaft member 532 and the driving wheel shaft 551 of the driving wheel 55 are axially supported by the base plate 11 and the train wheel bridge 14. As shown in fig. 7, a second hand shaft 941 is pivotally supported by the wheel train bridge 14 and by the base plate 11 via a minute wheel 921. That is, the second shaft 941, the eccentric shaft member 532, and the driving wheel shaft 551 of the driving wheel 55 are supported by the base plate 11 and the train wheel bridge 14. Therefore, the support members can be reduced as compared with the case where they are pivotally supported by separate support members, and therefore, the thickness of the timepiece 1 can be reduced.

[ 1 st and 2 nd reel ]

As shown in fig. 10, the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 are arranged in a plane direction perpendicular to the axial direction of the 1 st shaft 23 and the 2 nd shaft 33.

As described above, the 1 st barrel wheel 21 is connected to the manual winding train and the automatic winding train, and is therefore the most upstream barrel wheel as the drive source.

As described above, the 2 nd barrel wheel 31 is connected to the second wheel 92, and drives the hand moving mechanism of the minute second hand, and therefore, is the most downstream barrel wheel as the driving source.

The dimension of the plane of the 1 st can wheel 21 as viewed in the axial direction of the 1 st shaft 23 is set to be, specifically, the addendum circle diameter da1 is set to be smaller than the addendum circle diameter da2 of the 2 nd can wheel 31. In addition, the thickness H1 of the 1 st barrel 22 of the 1 st barrel 21 is thicker than the thickness H2 of the 2 nd barrel 32 of the 2 nd barrel 31.

The 2 nd barrel 32 of the 2 nd barrel 31 is engaged with the pinion of the second winding wheel 92 disposed at the center of the plane of the base plate 11, and is set to have a diameter as large as possible, that is, a size close to the radius of the base plate 11, within the range from the center of the plane of the base plate 11 to the outer periphery, as shown in fig. 4, in order to increase the number of turns of the 2 nd spring 30 as much as possible.

Further, since the 2 nd can 32 has a large planar size, the thickness thereof is set to be thin, and the winding display gear train 71 and the like can be arranged to overlap each other in a planar view.

Since the 1 st barrel 22 of the 1 st barrel reel 21 is set to have a small planar size of about 50 to 70% of the 2 nd barrel 32, it can be disposed in the space between the 2 nd barrel reel 31 and the manual winding mechanism 40 as shown in fig. 4, and the space is effectively utilized.

Here, the dimensions of the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 can be set as appropriate, and for example, the addendum circle diameter da1 of the 1 st barrel wheel 21 is 8.8mm, and the addendum circle diameter da2 of the 2 nd barrel wheel 31 is 16.0 mm. Therefore, the addendum circle diameter da2 of the 2 nd can wheel 31 is about 1.5 to 2.0 times larger than the addendum circle diameter da1 of the 1 st can wheel 21. Further, the inner diameter of barrel 1 22 for housing barrel 120 is, for example, 7.8mm, and the inner diameter of barrel 2 32 for housing barrel 2 30 is, for example, 15.0 mm.

The thickness H1 of the 1 st barrel 22 is, for example, 1.9mm, and the thickness H2 of the 2 nd barrel 32 is, for example, 1.6 mm. Accordingly, the thickness H1 of barrel 1 22 is about 1.1-1.5 times greater than the thickness H2 of barrel 2.

Winding spring 120 of barrel 1 drum 21 is wound by manual winding mechanism 40 or automatic winding mechanism 50. Winding 2 spring 30 of winding 2 drum 31 is wound up by the force of unwinding winding 1 spring 20.

Here, the force of unwinding of spring 1, 20, is transmitted from drum 1, 21, via drum intermediate 27, to drum 2, large drum 34, of

drum

2, 31. When the gear ratio of the transmission path between 1

st drum

21 and 2 nd drum 31 is set to 1, it is preferable that the winding torque of 1 st barrel 20 is larger than the winding torque of 2 nd barrel 30, that is, the winding torque of 1 st drum 21 is larger than the winding torque of 2 nd drum 31.

In the present embodiment, thickness of barrel spring 1 is 0.098mm, width of barrel spring 1 in thickness direction of barrel spring 22 (axial direction of barrel shaft 1 23) is 1.25mm, and maximum value of torque is about 62gcm (6.08 mNm).

The thickness of the 2 nd barrel 30 is 0.114mm, the width dimension in the thickness direction of the 2 nd barrel 32 (the axial direction of the 2 nd shaft 33) is 0.88mm, and the maximum value of the torque is about 56gcm (5.49 mNm).

Therefore, winding torque of 1 st spring 20 is set to be higher than winding torque of 2 nd spring 30 by about 10%.

The timepiece 1 of the present embodiment is an electronically controlled mechanical timepiece that uses a mechanism for adjusting the rotation of the rotor 81 of the generator 80 as a speed adjusting mechanism of the display train 90. Further, the 1 st spring 20 and the 2 nd spring 30 are used in a range where the torque is maintained at a certain level or more. For example, the number of turns of the 1 st spring 20 that maximizes the spring torque is about 6.5 turns, and the number of turns that decrease to a certain level, for example, 44gcm or less is about 4.5 turns, and is about 35 hours in terms of the duration of the timepiece 1.

The number of turns of the 2 nd spring 30 that maximizes the spring torque is about 15, and the number of turns of the spring torque that decreases to a certain level, for example, 42gcm or less is about 10.5, and is about 85 hours in terms of the duration of the timepiece 1.

The number of turns of the

springs

20 and 30 whose torque is reduced to the predetermined level or less can be obtained in advance by an experiment or the like, and the number of revolutions of the 2 nd drum 31 up to the number of turns can be grasped in advance. Thus, the charging needle 5 is set to: when the torque of each of the

springs

20 and 30 drops to the predetermined level or less, the duration is 0, and a stop mechanism such as a cam is provided in the energy accumulating wheel train 70, and the stop mechanism engages with the gear of the 2 nd barrel wheel 31 when the duration is 0, thereby stopping the rotation of the 2 nd barrel wheel 31.

The mechanism for stopping the rotation of the 2 nd barrel 31, that is, the 1 st barrel 21 is not limited to a mechanical mechanism using a cam or the like, and a control mechanism based on a control IC that applies short-circuit braking to the rotor 81 of the generator 80 and stops the same via the display train 90 may be used.

Since timepiece 1 has automatic winding mechanism 50, it is necessary to have a sliding mechanism in order to prevent breakage of the power spring due to excessive winding. Since 2 nd spring 30 is wound by 1 st spring 20, if a sliding mechanism is provided in 1 st spring 20, winding efficiency of 2 nd spring 30 decreases.

Therefore, the 1 st barrel spring 20 is fixed by locking the outer peripheral end of the 1 st barrel spring 20 to the notch provided in the inner peripheral surface of the 1 st barrel 22 without using a sliding mechanism. Further, the 2 nd spring 30 has a sliding mechanism, and the 2 nd spring 30 is fixed to the inner peripheral surface of the 2 nd barrel 32 by a sliding attachment 35.

Since the diameter of the 1 st reel 21 connected to the manual winding mechanism 40 and the automatic winding mechanism 50 is small, the winding torque tends to increase. In the present embodiment, the transmission wheel shaft 551 of the transmission wheel 55 and the 1 st barrel 22 are provided with a structure different from the conventional one without overlapping in plan view, and the transmission wheel 55 is a winding wheel which is wound around the 1 st barrel 21. This makes it possible to increase the diameter of the 1 st large steel wheel 24 meshing with the transmission wheel 55 as much as possible, and to suppress the winding torque. That is, in the present embodiment, the addendum circle diameter da3 of the 1 st large steel wheel 24 is set to be larger than the addendum circle diameter da1 of the 1 st can wheel 21.

[ Effect of the embodiment ]

According to the present embodiment, the following effects can be obtained.

The timepiece 1 of the present embodiment has the 1 st barrel wheel 21 and the 2 nd barrel wheel 31, and the rotation of the 1 st barrel wheel 21 is transmitted to the 2 nd barrel wheel 31. Therefore, the duration when winding 1 st spring 20 and winding 2 nd spring 30 are fully wound can be extended.

In the present embodiment, since the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 are arranged in a plane direction perpendicular to the axial direction of the 1 st barrel shaft 23, the thickness of the timepiece 1 can be reduced as compared with a case where the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 are arranged to overlap in the axial direction.

Further, since the diameter of the tip circle of the 1 st barrel wheel 21 is made smaller than the diameter of the tip circle of the 2 nd barrel wheel 31 and the thickness of the 1 st barrel 22 is made larger than the thickness of the 2 nd barrel 32, the arrangement space of the 1 st barrel wheel 21 and the 2 nd barrel wheel 31 can be effectively used in the movement 10, and the vacant space can be reduced.

Therefore, the timepiece 1 can be provided that is long in duration while suppressing an increase in the planar size and thickness of the timepiece 1. That is, since the 2 nd barrel wheel 31 connected to the second reel 92 is disposed in the range from the center position of the plane of the bottom plate 11 on which the second reel 92 is disposed to the outer periphery of the bottom plate 11, the number of turns of the 2 nd barrel 30 can be increased, and the duration of the timepiece 1 can be extended. Further, since the 2 nd can 32 is set to be thinner than the 1 st can 22, the winding display gear train 71 and the like can be arranged to overlap each other in a plan view, and the space can be effectively utilized.

Further, since the thickness of barrel 1 connected to manual winding mechanism 40 and automatic winding mechanism 50 is thicker than barrel 2 31, the width dimension of barrel 1 can be increased. Therefore, the thickness of the 1 st barrel 20 can be reduced, and even if the diameter of the 1 st barrel 22 is small, the torque balance can be established while securing the number of windings.

Since winding torque of barrel 1 21 is larger than winding torque of barrel 2 31, barrel 2 31 can be stably wound by barrel 1 21.

The 1 st spring 20 is fixed by engaging one end of the 1 st spring 20 with a notch provided in the inner peripheral surface of the 1 st barrel 22, and the 2 nd spring 30 is fixed to the inner peripheral surface of the 2 nd barrel 32 by a sliding attachment 35. Therefore, torque management at the time of complete wind-up of each of power springs 20 and 30 can be easily performed, and stable winding can be achieved.

Since the automatic winding mechanism 50 having the 1 st winding spring 20 winds the 1 st winding spring 20 and the driving wheel shaft 551 of the driving wheel 55 as the winding wheel of the automatic winding mechanism 50 does not overlap the 1 st barrel 22 in plan view, the timepiece 1 can be made thinner as compared with a configuration in which the shaft of the winding wheel overlaps the 1 st barrel 22 in plan view. Further, since the thickness of barrel 1 22 can be made relatively thick, the width of barrel 1 can be further increased.

Since the diameter of the addendum circle of the 1 st large steel wheel 24 fixed to the 1 st shaft 23 is set to be larger than that of the 1 st barrel wheel 21, the winding torque of the 1 st barrel wheel 21 having a small diameter can be reduced.

In the present embodiment, when the timepiece 1 is divided into two areas, i.e., the 1 st area including the time scale 3B indicating the 6 th time and the 2 nd area including the time scale 3B indicating the 12 th time by a line segment connecting the time scales 3B indicating the 3 rd time and the 9 th time of the dial 3 in plan view, the 1 st reel 21 and the 2 nd reel 31 are arranged in the 2 nd area. Therefore, the 1 st barrel reel 21 and the 2 nd barrel reel 31 do not interfere with the generator 80 and the like disposed in the 1 st region, and therefore, the layout of the components in the movement 10 can be easily performed.

In addition, since the 1 st barrel wheel 21 having a small diameter and the 2 nd barrel wheel 31 having a large diameter are disposed in the 2 nd region, the 2 nd region can be effectively utilized.

Further, in the movement 10, the remaining space where the 1 st barrel reel 21 and the 2 nd barrel reel 31 are disposed can be provided with the balance spring amount display mechanism, the feed mechanism, the governor mechanism, the power generation mechanism, and the like, so that the space can be effectively utilized.

[ modified examples ]

The present disclosure is not limited to the above embodiments, and modifications, improvements, and the like within a range that can achieve the object of the present disclosure are included in the present disclosure.

In the above embodiment, the timepiece 1 is configured as an electronically controlled mechanical timepiece having the generator 80 and the display train 90, but is not limited thereto. For example, the timepiece may be a mechanical timepiece having a normal speed regulating mechanism such as an escape wheel and a pallet fork.

In the embodiment, the winding torque of barrel 1 is larger than that of barrel 2 31, but may be the same value or may be a value slightly smaller than that of barrel 2 31.

In the above embodiment, the 1 st spring 20 is fixed to the inner peripheral surface of the 1 st barrel 22 by locking and the 2 nd spring 30 is fixed by using a sliding attachment, but the 1 st spring 20 may be fixed by using a sliding attachment, and the 2 nd spring 30 may be fixed to the inner peripheral surface of the 2 nd barrel 32.

In the above embodiment, the addendum circle diameter of the 1 st large steel wheel 24 is made larger than the addendum circle diameter of the 1 st barrel wheel 21, but the respective diameters may be made the same, or the addendum circle diameter of the 1 st large steel wheel 24 side may be made slightly smaller than the 1 st barrel wheel 21.

[ summary of the disclosure ]

The disclosed timepiece has: a1 st drum having a1 st shaft, a1 st spring, and a1 st barrel; and a2 nd barrel including a2 nd shaft, a2 nd spring, and a2 nd barrel, arranged in a plane direction perpendicular to an axial direction of the 1 st shaft, wherein rotation of the 1 st barrel is transmitted to the 2 nd barrel, a tip diameter of the 1 st barrel is smaller than a tip diameter of the 2 nd barrel, and a thickness of the 1 st barrel is thicker than a thickness of the 2 nd barrel.

This can suppress the planar size and thickness of the timepiece 1 and can extend the duration. Particularly, when 2 barrel wheels are arranged on a planar circular movement, the arrangement space can be effectively and flexibly used, and the vacant space can be reduced.

Further, since the thickness of the 1 st barrel drum connected to the manual winding mechanism and the automatic winding mechanism is thicker than the thickness of the 2 nd barrel drum, the width dimension of the 1 st spring can be increased. Therefore, the thickness of the 1 st barrel can be reduced, and even if the diameter of the 1 st barrel is small, the torque balance can be established while securing the number of windings.

In the timepiece of the present disclosure, the winding torque of the 1 st reel is larger than the winding torque of the 2 nd reel.

Thereby, the 2 nd barrel can be stably tightened by the 1 st barrel.

In the timepiece of the present disclosure, the 1 st spring is fixed by engaging one end of the 1 st spring in a notch provided in an inner peripheral surface of the 1 st barrel, and the 2 nd spring is fixed to an inner peripheral surface of the 2 nd barrel by a sliding attachment.

This makes it possible to easily manage the torque at the time of complete winding of each spring, and to realize stable winding.

The timepiece of the present disclosure includes an automatic winding mechanism that winds the 1 st winding spring, wherein the 1 st large steel wheel is fixed to the 1 st winding shaft, the automatic winding mechanism includes a winding wheel that meshes with the 1 st large steel wheel, and an axis of the winding wheel does not overlap with the 1 st barrel when viewed in a plane in an axial direction of the 1 st winding shaft.

Thus, the timepiece can be made thinner than a structure in which the winding wheel shaft overlaps the 1 st barrel when viewed in plan. Further, since the thickness of barrel 1 can be made relatively thick, the width of barrel 1 can be further increased.

In the timepiece of the present disclosure, a1 st large steel wheel is fixed to the 1 st shaft, and a tip circle diameter of the 1 st large steel wheel is larger than a tip circle diameter of the 1 st barrel wheel.

This can reduce the winding torque of the 1 st barrel drum 21 having a small diameter.

The timepiece of the present disclosure includes a dial having a plurality of scales recorded thereon, and when the timepiece is divided into two regions by a line segment connecting the scales at the time of 3 and the time of 9 of the dial when viewed from a plane perpendicular to the dial, the 1 st barrel wheel and the 2 nd barrel wheel are arranged in one region, and the speed adjustment mechanism for adjusting the speed of the gear train driven by the 1 st barrel wheel and the 2 nd barrel wheel is arranged in the other region.

Thus, the 1 st barrel wheel and the 2 nd barrel wheel arranged in one region do not interfere with the governor mechanism arranged in the other region, and therefore, the layout of the components in the movement can be easily performed. Further, since the 1 st reel having a small diameter and the 2 nd reel having a large diameter are disposed in one region, the space of one region can be effectively utilized.

Claims

1. A timepiece, comprising:

a1 st drum having a1 st shaft, a1 st spring, and a1 st barrel; and

a2 nd barrel wheel having a2 nd shaft, a2 nd spring, and a2 nd barrel, arranged in a plane direction perpendicular to an axial direction of the 1 st shaft, to which the 2 nd barrel wheel is transmitted rotation of the 1 st barrel wheel,

the diameter of the addendum circle of the 1 st can wheel is smaller than that of the 2 nd can wheel,

the thickness of the 1 st barrel is thicker than that of the 2 nd barrel.

2. The timepiece according to claim 1,

the winding torque of the 1 st drum is larger than that of the 2 nd drum.

3. The timepiece according to claim 1 or 2,

the 1 st barrel is fixed by engaging one end of the 1 st barrel with a notch provided in an inner peripheral surface of the 1 st barrel,

the 2 nd spring is fixed to the inner peripheral surface of the 2 nd barrel by a sliding attachment.

4. The timepiece according to claim 1,

the timepiece has an automatic winding mechanism that winds the 1 st winding spring,

a1 st large steel wheel is fixed on the 1 st shaft,

the automatic winding mechanism has a winding wheel engaged with the 1 st large steel wheel, and an axis of the winding wheel does not overlap with the 1 st barrel when viewed from a plane of axial direction of the 1 st axis.

5. The timepiece according to claim 1,

a1 st large steel wheel is fixed on the 1 st shaft,

the diameter of the addendum circle of the 1 st large steel wheel is larger than that of the addendum circle of the 1 st box wheel.

6. The timepiece according to claim 1,

the timepiece has a dial, which bears a plurality of scales,

when a timepiece is divided into two areas by a line segment connecting the scales at the time of 3 and 9 of the dial when viewed from a plane perpendicular to the dial, the 1 st barrel wheel and the 2 nd barrel wheel are arranged in one area, and a speed control mechanism for controlling the speed of a gear train driven by the 1 st barrel wheel and the 2 nd barrel wheel is arranged in the other area.